JPH08166025A - Friction plate wherein drag torque is reduced - Google Patents
Friction plate wherein drag torque is reducedInfo
- Publication number
- JPH08166025A JPH08166025A JP6331372A JP33137294A JPH08166025A JP H08166025 A JPH08166025 A JP H08166025A JP 6331372 A JP6331372 A JP 6331372A JP 33137294 A JP33137294 A JP 33137294A JP H08166025 A JPH08166025 A JP H08166025A
- Authority
- JP
- Japan
- Prior art keywords
- plate
- friction
- friction plate
- oil
- outer edge
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/648—Clutch-plates; Clutch-lamellae for clutches with multiple lamellae
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、湿式多板摩擦係合装置
に使用される摩擦板に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a friction plate used in a wet multi-plate friction engagement device.
【０００２】[0002]
【従来の技術】湿式多板摩擦係合装置は、車両のオート
マティックトランスミッション等に用いられている。図
６に示されるように、この種の摩擦係合装置５０は、交
互に配設された摩擦板５２及びメイティングプレート５
４と、摩擦板５２とメイティングプレート５４とを係合
させる油圧作動式ピストン５６を有してなる。2. Description of the Related Art Wet multi-plate friction engagement devices are used in automatic transmissions of vehicles. As shown in FIG. 6, this type of friction engagement device 50 includes a friction plate 52 and a mating plate 5 that are alternately arranged.
4 and a hydraulically actuated piston 56 for engaging the friction plate 52 and the mating plate 54.
【０００３】[0003]
【発明が解決しようとする課題】同図のように、非係合
状態の摩擦板５２とメイティングプレート５４の間で
は、理論上、トルクは伝達されない。ところが、実際に
は、摩擦板５２とメイティングプレート５４との間に油
が介在するため、この油によって、摩擦板５２からメイ
ティングプレート５４へ、又はメイティングプレート５
４から摩擦板５２へ、少なからずトルクが伝達される。
このように伝達されるトルクをドラグトルクといい、例
えば、オートマティックトランスミッションでは動力損
失の原因となっている。本発明の目的は、このようなド
ラグトルクを低減することである。As shown in the figure, theoretically, no torque is transmitted between the friction plate 52 and the mating plate 54 in the non-engaged state. However, in reality, since oil is present between the friction plate 52 and the mating plate 54, this oil causes the friction plate 52 to move to the mating plate 54 or the mating plate 5
Torque is transmitted from 4 to the friction plate 52.
The torque transmitted in this way is called drag torque, which causes power loss in, for example, an automatic transmission. An object of the present invention is to reduce such drag torque.
【０００４】[0004]
【課題を解決するための手段】本発明は、第１に、コア
プレートに摩擦材が固着された摩擦板とメイティングプ
レートとが油中で係合することによりトルク伝達を行う
摩擦係合装置に使用される摩擦板において、該摩擦材の
表面に、内縁から外縁に貫通して延び且つ前記内縁及び
外縁より中央部の深さを浅くした放射状の油溝を設けた
摩擦板により前記課題を解決した。SUMMARY OF THE INVENTION The first aspect of the present invention is a friction engagement device for transmitting torque by engaging a friction plate having a friction material fixed to a core plate and a mating plate in oil. In the friction plate used for the above, the above-mentioned problem is solved by a friction plate provided on the surface of the friction material with a radial oil groove extending from the inner edge to the outer edge and having a shallower central portion depth than the inner edge and the outer edge. Settled.
【０００５】本発明は、第２に、コアプレートに摩擦材
が固着された摩擦板とメイティングプレートとが油中で
係合することによりトルクの伝達を行う摩擦係合装置に
使用される摩擦板において、前記摩擦材の表面に、内縁
から外縁に貫通して延び且つ前記内縁及び外縁より中央
部の幅が狭くなるように周方向に対称な円弧で区画した
油溝を設けた摩擦板により前記課題を解決した。Secondly, the present invention relates to a friction engagement device for transmitting torque by engaging a friction plate having a friction material fixed to a core plate and a mating plate in oil. In the plate, a friction plate is provided on the surface of the friction material, the oil groove extending from the inner edge to the outer edge and having an oil groove defined by arcs symmetrical in the circumferential direction so that the width of the central portion is narrower than the inner edge and the outer edge. The said subject was solved.
【０００６】本発明は、第３に、コアプレートに摩擦材
が固着された摩擦板とメイティングプレートとが油中で
係合することによりトルクの伝達を行う摩擦係合装置に
使用される摩擦板において、該摩擦材の表面に、内縁か
ら外縁に貫通して延び且つ前記内縁及び外縁より中央部
を周方向に膨らませた円弧状溝を設けた摩擦板により前
記課題を解決した。Thirdly, the present invention relates to a frictional engagement device for transmitting torque by engaging a friction plate having a friction material fixed to a core plate and a mating plate in oil. In the plate, the above problem is solved by a friction plate having an arc-shaped groove extending from the inner edge to the outer edge on the surface of the friction material and bulging the central portion in the circumferential direction from the inner edge and the outer edge.
【０００７】[0007]
【作用】摩擦材表面に上述のような特定形状の溝を設け
ることにより、摩擦板とメイティングプレートとの間の
油の圧力が周辺より高くなる。すなわち、摩擦板とメイ
ティングプレートとの間に正圧が発生し、この圧力は摩
擦板とメイティングプレートとを離反させようとする。
その結果、ドラグトルクを軽減することができる。By providing the groove of the above-mentioned specific shape on the surface of the friction material, the pressure of the oil between the friction plate and the mating plate becomes higher than that of the periphery. That is, a positive pressure is generated between the friction plate and the mating plate, and this pressure tends to separate the friction plate and the mating plate.
As a result, drag torque can be reduced.
【０００８】第１の発明では、摩擦材表面の油溝を通じ
て油が内縁から外縁に流れるとき、油溝の断面積が縮小
するので、中央部で圧縮された油が摩擦板とメイティン
グプレートとを離反させようとする。この圧力によって
摩擦板とメイティングプレートとの隙間が大きくなり、
ドラグトルクが低減される。In the first aspect of the invention, when the oil flows from the inner edge to the outer edge through the oil groove on the surface of the friction material, the cross-sectional area of the oil groove is reduced, so that the oil compressed at the central portion becomes the friction plate and the mating plate. Try to separate. This pressure increases the gap between the friction plate and the mating plate,
Drag torque is reduced.
【０００９】第２の発明では、油溝の断面積が第１の発
明と同様に中央部で小さくなる。従って、油が油溝を通
過するとき、断面積が縮小する中央部で油の圧力が高く
なり、摩擦板とメイティングプレートとが離反させられ
る。In the second invention, the cross-sectional area of the oil groove is reduced in the central portion as in the first invention. Therefore, when the oil passes through the oil groove, the pressure of the oil increases at the central portion where the cross-sectional area is reduced, and the friction plate and the mating plate are separated from each other.
【００１０】第３の発明では、円弧状溝が回転方向の逆
方向に膨らむように、摩擦板を取り付けることにより、
摩擦板の空転時に、内縁では油溝への油の流入が促進さ
れ、外縁では油溝からの油の流出が制限されて、油溝内
の圧力が周辺の圧力より高くなる。油溝内の油に生じる
圧力は摩擦板とメイティングプレートとを離反させる。
その結果、第１及び第２の発明と同様に、ドラグトルク
が低減される。In the third aspect of the invention, the friction plate is attached so that the arcuate groove bulges in the direction opposite to the rotation direction.
When the friction plate idles, the inflow of oil into the oil groove is promoted at the inner edge and the outflow of oil from the oil groove is restricted at the outer edge, so that the pressure inside the oil groove becomes higher than the pressure in the surroundings. The pressure generated in the oil in the oil groove separates the friction plate and the mating plate.
As a result, the drag torque is reduced as in the first and second aspects of the invention.
【００１１】[0011]
【実施例】図１及び図２は、本発明による摩擦板の第１
実施例を示している。摩擦板１０は、スプライン１２が
形成されたコアプレート１４と、その表面に固着された
摩擦材１６からなる。摩擦材１６の表面には、複数の放
射状の油溝１８が形成されている。放射状の油溝１８
は、摩擦材１６の内縁から外縁に貫通して延びており、
その断面形状は矩形である。そして、油溝１８の深さ
は、内縁から中央部に向って徐々に浅くなり、中央部か
ら外縁に向って徐々に深くなっている。なお、同図の油
溝１８は断面形状が矩形であるが、その断面形状を、例
えば、半円形とすることができる。1 and 2 show a first friction plate according to the present invention.
An example is shown. The friction plate 10 is composed of a core plate 14 on which splines 12 are formed, and a friction material 16 fixed to the surface thereof. A plurality of radial oil grooves 18 are formed on the surface of the friction material 16. Radial oil groove 18
Extends from the inner edge of the friction material 16 to the outer edge thereof,
Its cross-sectional shape is rectangular. The depth of the oil groove 18 gradually decreases from the inner edge toward the central portion, and gradually increases from the central portion toward the outer edge. Although the oil groove 18 in the figure has a rectangular cross-sectional shape, the cross-sectional shape can be, for example, a semicircle.
【００１２】摩擦係合装置が係合状態から非係合状態に
移行するときは、ピストンに作用する油圧がなくなるだ
けであるから、摩擦板１０とメイティングプレートはす
ぐ隣合った状態にある。従って、摩擦板１０とメイティ
ングプレートとの間の相対回転は、動力損失の原因とな
るドラグトルクを発生させる。When the friction engagement device shifts from the engagement state to the non-engagement state, the hydraulic pressure acting on the piston is simply lost, so that the friction plate 10 and the mating plate are immediately adjacent to each other. Therefore, the relative rotation between the friction plate 10 and the mating plate generates drag torque that causes power loss.
【００１３】本発明では、摩擦板１０とメイティングプ
レートの少なくとも一方が回転しているとき、油が遠心
力によって油溝１８を通じて摩擦材の内縁から外縁に流
れる。油溝１８は中央部で断面積が縮小しているので、
摩擦材１６の中央部の油溝１８における圧力はその周囲
の圧力より高くなる。摩擦板１０とメイティングプレー
トはこの圧力（正圧）によって離反させられ、ドラグト
ルクが低減される。In the present invention, when at least one of the friction plate 10 and the mating plate is rotating, oil flows from the inner edge of the friction material to the outer edge of the friction material through the oil groove 18 due to centrifugal force. Since the cross-sectional area of the oil groove 18 is reduced in the central portion,
The pressure in the oil groove 18 at the center of the friction material 16 becomes higher than the pressure around it. The friction plate 10 and the mating plate are separated from each other by this pressure (positive pressure), and the drag torque is reduced.
【００１４】図３は本発明による摩擦板の第２実施例を
示している。本実施例の摩擦板２０における油溝２８
は、内縁から外縁に貫通して延び、中央部が幅狭になっ
ている。本実施例の摩擦板２０の場合、油溝２８の深さ
は一定であり、幅のみが内縁から外縁にかけて変化して
いる。油溝２８は、次のような円弧が対向して形成され
ている。この円弧は、Ｒ１の半径の円弧とＲ２の半径の
円弧とが内縁と外縁の中間で連続した形状である。従っ
て、油が摩擦材２６の内縁から外縁に向って流れると
き、断面積が縮小する部分で油の圧力が高くなり、摩擦
板２０とメイティングプレートとが離反させられる。FIG. 3 shows a second embodiment of the friction plate according to the present invention. Oil groove 28 in the friction plate 20 of the present embodiment
Extends from the inner edge to the outer edge and has a narrow central portion. In the case of the friction plate 20 of this embodiment, the depth of the oil groove 28 is constant and only the width changes from the inner edge to the outer edge. The oil grooves 28 are formed so that the following arcs face each other. This arc has a shape in which an arc having a radius of R1 and an arc having a radius of R2 are continuous between the inner edge and the outer edge. Therefore, when the oil flows from the inner edge to the outer edge of the friction material 26, the pressure of the oil increases at the portion where the cross-sectional area decreases, and the friction plate 20 and the mating plate are separated from each other.
【００１５】なお、Ｒ１＜Ｒ２とすることにより、油溝
２８の内縁の幅Ｌ１は、外縁の幅Ｌ２より大きくなる。
油溝２８の形状をこのようにすることにより、多くの油
を油溝２８内に取り込んで油溝内に発生する油圧を一層
高めることができる。By setting R1 <R2, the width L1 of the inner edge of the oil groove 28 becomes larger than the width L2 of the outer edge thereof.
By setting the shape of the oil groove 28 in this way, much oil can be taken into the oil groove 28 and the hydraulic pressure generated in the oil groove can be further increased.
【００１６】図４は本発明による摩擦板の第３実施例を
示している。本実施例の摩擦板３０における油溝３８
は、内縁から外縁に貫通して延び、内縁及び外縁より中
央部が周方向に膨んだ円弧状溝である。油溝３８の断面
形状は特に限定されず、半円形又は矩形が一般的であ
る。FIG. 4 shows a third embodiment of the friction plate according to the present invention. Oil groove 38 in the friction plate 30 of the present embodiment
Is an arcuate groove that extends from the inner edge to the outer edge and has a central portion that bulges in the circumferential direction from the inner edge and the outer edge. The cross-sectional shape of the oil groove 38 is not particularly limited and is generally a semicircle or a rectangle.
【００１７】本実施例の摩擦板は、円弧が回転方向と逆
の方向に膨らむように装着することで、油溝３８内に正
圧を発生させることができる。すなわち、摩擦板３０が
矢印方向に回転すると、内縁では油が油溝３８に流れ込
み、外縁では油溝３８からの油の流出が制限されて、油
溝３８内の油圧が周囲より高くなる。この油圧は摩擦板
３０とメイティングプレートとを離反させる。その結
果、ドラグトルクが低減される。The friction plate of this embodiment is mounted so that the circular arc swells in the direction opposite to the rotation direction, so that a positive pressure can be generated in the oil groove 38. That is, when the friction plate 30 rotates in the direction of the arrow, oil flows into the oil groove 38 at the inner edge and the outflow of oil from the oil groove 38 is restricted at the outer edge, so that the oil pressure in the oil groove 38 becomes higher than the surroundings. This hydraulic pressure separates the friction plate 30 and the mating plate. As a result, drag torque is reduced.
【００１８】図５の摩擦板４０は、図４のような円弧状
の油溝４８，４９が交互に設けられたものである。中央
部が反時計回りに膨らむ円弧状の油溝４８は、摩擦板４
０が時計回りに回転するとき、油溝４８内に正圧を発生
させる。一方、中央部が時計回りに膨らむ円弧状の油溝
４９は、摩擦板４０が反時計回りに回転するとき、油溝
４９内に正圧を発生させる。このような油溝４８，４９
は、摩擦板４０がいずれの方向に回転するときにも油溝
４８，４９内に正圧を発生させる。この正圧は、前述の
実施例と同様に摩擦板４０とメイティングプレートとを
離反させるように作用する。その結果、ドラグトルクが
低減される。The friction plate 40 shown in FIG. 5 has arcuate oil grooves 48 and 49 provided alternately as shown in FIG. The arc-shaped oil groove 48 whose central portion swells counterclockwise is formed by the friction plate 4.
When 0 rotates clockwise, a positive pressure is generated in the oil groove 48. On the other hand, the arc-shaped oil groove 49 with the central portion swelling clockwise generates positive pressure in the oil groove 49 when the friction plate 40 rotates counterclockwise. Such oil grooves 48, 49
Generates a positive pressure in the oil grooves 48, 49 when the friction plate 40 rotates in either direction. This positive pressure acts to separate the friction plate 40 and the mating plate from each other, as in the above-described embodiment. As a result, drag torque is reduced.
【００１９】[0019]
【発明の効果】請求項１の発明では、油が摩擦板の油溝
を通過するとき、深さが浅くなった中央部で油圧が高く
なり、その油圧が摩擦板とメイティングプレートとを離
反させる。その結果、摩擦板とメイティングプレートと
の間隔が広くなり、ドラグトルクが低減する。According to the first aspect of the invention, when the oil passes through the oil groove of the friction plate, the hydraulic pressure becomes high at the central portion where the depth becomes shallow, and the hydraulic pressure separates the friction plate and the mating plate. Let As a result, the distance between the friction plate and the mating plate becomes wider, and the drag torque is reduced.
【００２０】請求項２の発明では、油が摩擦板の油溝を
通過するとき、幅が狭くなった中央部で油圧が高くな
り、その油圧が摩擦板とメイティングプレートとを離反
させる。その結果、摩擦板とメイティングプレートとの
間隔が広くなり、ドラグトルクが低減する。According to the second aspect of the present invention, when the oil passes through the oil groove of the friction plate, the hydraulic pressure becomes high at the central portion having the narrow width, and the hydraulic pressure separates the friction plate and the mating plate. As a result, the distance between the friction plate and the mating plate becomes wider, and the drag torque is reduced.
【００２１】請求項３の発明では、摩擦板とメイティン
グプレートとが相対回転を生じるときに、円弧状溝内の
油の油圧がその周辺の油圧より高くなるので、その油圧
が摩擦板とメイティングプレートとを離反させる。その
結果、摩擦板とメイティングプレートとの間隔が広くな
り、ドラグトルクが低減する。According to the third aspect of the present invention, when the friction plate and the mating plate rotate relative to each other, the oil pressure of the oil in the arcuate groove becomes higher than the oil pressure in the periphery thereof. Away from the tongue plate. As a result, the distance between the friction plate and the mating plate becomes wider, and the drag torque is reduced.
【図１】 本発明による摩擦板の第１実施例を示す平面
図。FIG. 1 is a plan view showing a first embodiment of a friction plate according to the present invention.
【図２】 図１の摩擦板の一部拡大斜視図。FIG. 2 is a partially enlarged perspective view of the friction plate of FIG.
【図３】 本発明による摩擦板の第２実施例を示す平面
図。FIG. 3 is a plan view showing a second embodiment of the friction plate according to the present invention.
【図４】 本発明による摩擦板の第３実施例を示す平面
図。FIG. 4 is a plan view showing a third embodiment of the friction plate according to the present invention.
【図５】 本発明による摩擦板の第４実施例を示す平面
図。FIG. 5 is a plan view showing a fourth embodiment of the friction plate according to the present invention.
【図６】 一般的な湿式摩擦係合装置の断面図。FIG. 6 is a cross-sectional view of a general wet friction engagement device.
１０，２０，３０，４０ 摩擦板 １２ スプライン １４ コアプレート １６ 摩擦材 １８，２８，３８，４８ 油溝 10, 20, 30, 40 Friction plate 12 Spline 14 Core plate 16 Friction material 18, 28, 38, 48 Oil groove
Claims (3)
板とメイティングプレートとが油中で係合することによ
りトルク伝達を行う摩擦係合装置に使用される摩擦板に
おいて、 前記摩擦材の表面に、内縁から外縁に貫通して延び且つ
前記内縁及び外縁より中央部の深さを浅くした放射状の
油溝を設けたことを特徴とする、 摩擦板。1. A friction plate used in a friction engagement device for transmitting torque by engaging a friction plate having a friction material fixed to a core plate in oil with a mating plate, wherein A friction plate, characterized in that a radial oil groove is provided on the surface, the radial oil groove extending from the inner edge to the outer edge and having a depth of a central portion shallower than the inner edge and the outer edge.
板とメイティングプレートとが油中で係合することによ
りトルクの伝達を行う摩擦係合装置に使用される摩擦板
において、 前記摩擦材の表面に、内縁から外縁に貫通して延び且つ
前記内縁及び外縁より中央部の幅が狭くなるように周方
向に対称な円弧で区画した油溝を設けたことを特徴とす
る、 摩擦板。2. A friction plate used in a friction engagement device, wherein a friction plate having a friction material fixed to a core plate and a mating plate engage with each other in oil to transmit torque. The friction plate is characterized in that an oil groove extending through the inner edge to the outer edge and having a central portion narrower than the inner edge and the outer edge is divided by arcs symmetrical in the circumferential direction.
板とメイティングプレートとが油中で係合することによ
りトルクの伝達を行う摩擦係合装置に使用される摩擦板
において、 該摩擦材の表面に、内縁から外縁に貫通して延び且つ前
記内縁及び外縁より中央部を周方向に膨らませた円弧状
溝を設けたことことを特徴とする、 摩擦板。3. A friction plate used in a friction engagement device, wherein a friction plate having a friction material fixed to a core plate and a mating plate engage with each other in oil to transmit torque, the friction plate comprising: An arcuate groove extending from the inner edge to the outer edge and bulging in the central portion in the circumferential direction from the inner edge and the outer edge is provided on the surface of the friction plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6331372A JPH08166025A (en) | 1994-12-12 | 1994-12-12 | Friction plate wherein drag torque is reduced |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6331372A JPH08166025A (en) | 1994-12-12 | 1994-12-12 | Friction plate wherein drag torque is reduced |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08166025A true JPH08166025A (en) | 1996-06-25 |
Family
ID=18242954
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6331372A Pending JPH08166025A (en) | 1994-12-12 | 1994-12-12 | Friction plate wherein drag torque is reduced |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08166025A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6499579B2 (en) * | 2000-04-13 | 2002-12-31 | Aisin Kako Kabushiki Kaisha | Wet type friction member |
| US6753702B2 (en) | 2001-08-29 | 2004-06-22 | Nec Electronics Corporation | Semiconductor integrated circuit and its layout method |
| WO2005085667A1 (en) * | 2004-03-04 | 2005-09-15 | Kabushiki Kaisha F.C.C. | Wet type clutch friction plate |
| JP2005265186A (en) * | 2004-02-18 | 2005-09-29 | Dainatsukusu:Kk | Optimization method for groove structure of friction plate of wet type friction engagement element |
| JP2007132362A (en) * | 2005-11-08 | 2007-05-31 | Nsk Warner Kk | Friction plate and wet multi-disk clutch with friction plate |
| DE19959010B4 (en) * | 1999-12-08 | 2011-12-29 | Zf Sachs Ag | coupling device |
| EP2994661B1 (en) | 2013-05-06 | 2017-12-27 | Schaeffler Technologies AG & Co. KG | Clutch having reduced drag torque |
-
1994
- 1994-12-12 JP JP6331372A patent/JPH08166025A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19959010B4 (en) * | 1999-12-08 | 2011-12-29 | Zf Sachs Ag | coupling device |
| US6499579B2 (en) * | 2000-04-13 | 2002-12-31 | Aisin Kako Kabushiki Kaisha | Wet type friction member |
| US6753702B2 (en) | 2001-08-29 | 2004-06-22 | Nec Electronics Corporation | Semiconductor integrated circuit and its layout method |
| JP2005265186A (en) * | 2004-02-18 | 2005-09-29 | Dainatsukusu:Kk | Optimization method for groove structure of friction plate of wet type friction engagement element |
| WO2005085667A1 (en) * | 2004-03-04 | 2005-09-15 | Kabushiki Kaisha F.C.C. | Wet type clutch friction plate |
| EP1731784A1 (en) † | 2004-03-04 | 2006-12-13 | Kabushiki Kaisha F.C.C. | Wet type clutch friction plate |
| US8061498B2 (en) | 2004-03-04 | 2011-11-22 | Kabushiki Kaisha F.C.C. | Wet clutch friction plate |
| EP1731784B2 (en) † | 2004-03-04 | 2014-03-05 | Kabushiki Kaisha F.C.C. | Wet type clutch friction plate |
| JP2007132362A (en) * | 2005-11-08 | 2007-05-31 | Nsk Warner Kk | Friction plate and wet multi-disk clutch with friction plate |
| EP2994661B1 (en) | 2013-05-06 | 2017-12-27 | Schaeffler Technologies AG & Co. KG | Clutch having reduced drag torque |
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